High capacity cargo and container dolly

ABSTRACT

A high capacity cargo/container dolly. The cargo/container dolly includes retractable side stops that actively retract a roller linkage assembly upon retraction of the retractable side stops rather than relying on passive gravitational forces for the retraction. In some embodiments, the retractable side stops are configured to avoid hold up on the cargo during retraction. The retractable side stops may be coupled to a retraction mechanism that may be actuated from either side of the cargo/container dolly, as well as from one or both ends of the cargo/container dolly. The dolly may include aspects that accommodates dynamic loads that occur during transport to mitigate inadvertent retraction of the retractable side stops or spurious release of catch assemblies that retains cargo on the dolly. The dolly may also include self-locking roller assemblies that release only in the presence of cargo, and deck modules that protect the deck roller from road spray contamination.

RELATED APPLICATIONS

This patent application is a continuation-in-part of InternationalApplication No. PCT/US2018/063277, filed Nov. 30, 2018, which claims thebenefit of U.S. Provisional Application No. 62/593,797, filed Dec. 1,2017, U.S. Provisional Application No. 62/732,266, filed Sep. 17, 2018,U.S. Provisional Application No. 62/746,304, filed Oct. 16, 2018, andU.S. Provisional Application No. 62/754,196, filed Nov. 1, 2018, thedisclosures of which are hereby incorporated by reference herein intheir entirety. This patent application also claims the benefit of U.S.Provisional Application No. 62/797,739, filed Jan. 28, 2019, thedisclosure of which is hereby incorporated by reference herein in itsentirety.

BACKGROUND

Freight aircraft are often loaded and unloaded using two differentdollies: “cargo dollies” and “container dollies.” Cargo dollies aredesigned for loading and unloading large, heavy cargo into the wide,main deck of the aircraft. Examples of the containers that are loadedwith cargo dollies include 224- by 318-centimeter (88- by 125-inch)containers and 244- by 318-centimeter (96- by 125-inch) containers. Forcargo dollies, weight capacity and volume are at a premium to handlesuch containers. Container dollies are designed for loading andunloading smaller containers into the lower deck or “belly” of theaircraft. Examples of the containers that are loaded with containerdollies include the LD2, LD3, and LD8. For container dollies,maneuverability and low clearance profile are at a premium toaccommodate loading and unloading of cargo into the belly of aircraft.

Maintaining two fleets of dollies is duplicative and expensive. A dollythat can accommodate the capacity of cargo dollies while having themaneuverability and low clearance profile to perform as containerdollies would be welcome.

SUMMARY

Various embodiments of the disclosure present a high capacitycargo/container dolly that performs the functions of both a cargo dollyand a container dolly. The disclosed cargo/container dolly is suited forthe high capacity of cargo dollies (up to 15,000 pounds of weight) whilehaving the maneuverability and low clearance profile of containerdollies.

In addition, some embodiments include improvements to the functionalityof certain components. Cargo dollies feature retractable side stops thatcontain cargo on the roller deck during transport and prevent cargo frombeing inadvertently rolled off the side of the dolly. The retractableside stops are retracted by operating personnel to offload thecontainer. A restriction placed on cargo dollies is a maximum width of102 inches, while the containers may be up to 96 inches in width.Accordingly, only a three inch operating envelope for the retractableside stops is provided on either side of the cargo dolly when handlingcontainers of 96 inches width. Specifications require at least one inchmargin on either side of a container to accommodate misalignment of thecontainers after loading, providing only a two inch width within whichthe retractable side stops must operate when handling containers of 96inches width. Conventional retractable side stops can encroach on theone inch margin during retraction, such that when misalignment requiresthe full one inch margin, conventional retractable side stops cancollide with and be “held up” by the container, preventing fullretraction. When such hold up occurs, conventional retractable sidestops can interfere with the offloading of the cargo container. Variousembodiments of the disclosure include retractable side stops that havebeen modified to assure that the one inch margin available for 96 inchcontainers is not encroached, thereby eliminating the possibility ofhold up on the container.

Conventional retractable side stops also rely in part on gravity toprovide a full retraction. Over time, the mechanisms that relies onpassive gravitational forces for proper operation can foul, causingcertain components of the conventional retractable side stops to “hangup” and fail to retract. When components fail to fully retract, theconventional retractable side stops can interfere with the offloading ofthe cargo container. Various embodiments of the disclosed high capacitycargo/container dolly include retractable side stops that activelyretract all components, and provides this feature within the two inchoperating envelope available for retractable side stops, therebymitigating the problems associated with the hang up of conventionalretractable side stops that rely on passive gravitational forces forproper operation.

Various embodiments of the disclosure include an auxiliary or bypassretraction mechanism that selectively retracts the retractable sidestops on only one side of the high capacity cargo/container dolly. Theauxiliary retraction mechanism may be accessible from a front end of thehigh capacity cargo/container dolly, a back end of the high capacitycargo/container dolly, or both the front and the back end. The auxiliaryretraction mechanism provides an alternative way to retract theretractable side stops when a given retraction mechanism provided on aside of the high capacity cargo/container dolly is inaccessible.

Various embodiments of the disclosure counter dynamic loads (e.g.,jostling or jolting while being transported over uneven terrain orobstacles) that may otherwise cause the retractable side stops tospuriously retract during transport. We have found that, under suchdynamic loading, the inertia of the retraction mechanisms and movingcomponents of the retractable side stops can actually cause theretractable side stops to retract and release. Unchecked, such spuriousretraction could cause containers to become unmoored and roll off theroller deck, for example when pulling the dolly through a turn. Variousembodiments of the disclosure include ways to counter inadvertentrelease of cargo during the rigors of transport. Some embodimentscounterbalance the weight of the retraction mechanisms and movingcomponents of the retractable side stops, the counterbalance thencountering the inertia of these components during an impact load. Someembodiments of the disclosure include biasing that counters the inertiagenerated by dynamic loads. Alternatively or in addition, someembodiments of the disclosure are designed to undergo verticaldeflections that are greater relative to conventional retractable sidestops before release of the cargo, thereby providing a greater toleranceto dynamic loading.

In various embodiments of the disclosure, the high capacitycargo/container dolly includes a plurality of deck modules that togethermake up a roller deck. In some embodiments, the deck modules includeself-locking roller assemblies. The self-locking roller assemblies maybe disposed proximate the edges of the high capacity cargo/containerdolly, and are able to roll only when actuated by a sliding planarobject, such as a container or pallet. As such, if operating personnelinadvertently step on a self-locking roller assembly, the roller remainslocked, so that the operating personnel will not lose their footing.

Structurally, various embodiments of a high capacity cargo/containerdolly are disclosed including a framework with an outer frame havingopposed side beam assemblies separated by a forward beam assembly and arearward beam assembly, a roller deck including a plurality of swivelcasters having upper extremities that define and are coplanar with aregistration plane, the registration plane being generally horizontal,and a side stop disposed proximate one of the opposed side beamassemblies. In some embodiments, the side stop includes a housing, aplunger assembly translatable in a vertical direction within thehousing, the plunger assembly including a platform portion, and a rollerlinkage assembly pivotally coupled to the housing about a pivot axis.The roller linkage assembly may include a pivot arm pivotal about thepivot axis and having a first end and a second end, a first rollerdisposed at the first end of the pivot arm that contacts the platformportion of the plunger assembly, and a second roller disposed at asecond end of the pivot arm that extends above the registration plane.An actuation member may be operatively coupled to the plunger assemblyand configured to contact the roller linkage assembly when the plungerassembly is translated downward into the housing and if the pivot armdoes not rotate about the pivot axis due to gravity.

In various embodiments of the disclosure, a retractable side stop of thehigh capacity cargo/container dolly includes a stop bracket mounted tothe housing that defines an uppermost position of the plunger assembly,a stop finger coupled to the plunger assembly and defining a verticalstop plane, and a catch assembly including a hook that extends upwardfrom a lever, the lever being mounted to a pivot that is coupled to theplunger assembly, the lever including a laterally inward portion thatdefines a length having a lateral dimension that extends from the pivottoward the centerline of the framework, the laterally inward portion ofthe lever extending underneath the stop bracket. In a captureconfiguration, the laterally inward portion of the lever of the catchassembly is engaged in contact with the stop bracket and the hook of thecatch assembly extends above the registration plane and a bend portionof the hook extends laterally inward relative to the vertical stopplane. In a release configuration, the bend portion of the hook ispositioned entirely laterally outward relative to the vertical stopplane, the laterally inward portion of the lever being configured todisengage from contact with the stop bracket to attain the releaseconfiguration when the plunger assembly is translated axially downwardrelative to the uppermost position. In some embodiments, the laterallyinward portion of the lever is configured to disengage from contact withthe stop bracket when the plunger assembly is translated a minimumdownward vertical displacement from the uppermost position, the minimumdownward vertical displacement being in a range of ⅝ inch to 1½ inchinclusive. In some embodiments, the minimum downward verticaldisplacement being in a range of ¾ inch to 1 inch inclusive.

Various embodiments of a high capacity cargo/container dolly include aframework with an outer frame having opposed side beam assembliesseparated by a forward beam assembly and a rearward beam assembly, theframework defining a centerline that extends from the forward beamassembly to the rearward beam assembly and is equidistant between theopposing side beam assemblies. A roller deck includes a plurality ofswivel casters having upper extremities that define and are coplanarwith a registration plane, the registration plane being generallyhorizontal. In some embodiments, a retractable side stop is disposedproximate one of the opposed side beam assemblies and is configurable ina deployed configuration and a retracted configuration. The retractableside stop may include a housing, a plunger assembly translatable in avertical direction within the housing, the plunger assembly including aplatform portion, a stop finger coupled to the plunger assembly anddefining a vertical stop plane, the vertical stop plane intersecting theregistration plane at an intersection line, the intersection line beingsubstantially parallel to the centerline, and a roller linkage assemblypivotally coupled to the housing about a pivot axis. In the deployedconfiguration, the roller linkage assembly extends through theregistration plane and is disposed laterally outward relative to thecenterline from the intersection line. In the retracted configuration,the roller linkage assembly is rotated completely below the registrationplane. In some embodiments, in transitioning the retractable side stopfrom the deployed configuration to the retracted configuration, theroller linkage assembly is rotated completely below the registrationplane without crossing the intersection line.

Various embodiments of a high capacity cargo/container dolly include aframework including an outer frame having opposed side beam assembliesseparated by a forward beam assembly and a rearward beam assembly, aroller deck including a plurality of swivel casters having upperextremities that define and are coplanar with a registration plane, theregistration plane being generally horizontal, and a retractable sidestop disposed proximate one of the opposed side beam assemblies. Theretractable side stop includes a housing, a plunger assemblytranslatable in a vertical direction within the housing, the plungerassembly including a platform portion, a stop finger coupled to theplunger assembly, and a roller linkage assembly pivotally coupled to thehousing about a pivot axis. The roller linkage assembly may include apivot arm pivotal about the pivot axis and having a first end and asecond end, a first roller disposed at the first end of the pivot armthat contacts the platform portion of the plunger assembly, and a secondroller disposed at a second end of the pivot arm that extends above theregistration plane. The retractable side stop may include means forrotating the roller linkage assembly about the pivot axis if the rollerlinkage assembly does not rotate about the pivot axis due to gravity. Insome embodiments, the means for rotating the roller linkage assemblyabout the pivot axis includes an actuation member coupled to the stopfinger, the actuation member configured to contact the roller linkageassembly if the roller linkage assembly does not rotate about the pivotaxis due to gravity. In one embodiment, the actuation member contacts anextension tab that extends from the roller linkage assembly into atranslation path of the actuation member if the roller linkage assemblydoes not rotate about the pivot axis due to gravity. In anotherembodiment, the actuation member contacts the pivot arm of the rollerlinkage assembly if the roller linkage assembly does not rotate aboutthe pivot axis due to gravity. The pivot arm may include a cam surfacefor contact with the actuation member, the cam surface defining arecess. In some embodiments, the retractable side stops are mounted tothe one of the opposed side beam assemblies.

Various embodiments of a high capacity cargo/container dolly include aframework including an outer frame having opposed side beam assembliesseparated by a forward beam assembly and a rearward beam assembly, afirst retractable side stop coupled to a first of the opposed side beamassemblies, a first foot actuated retraction mechanism operativelycoupled to the first retractable side stop, a second retractable sidestop coupled to the second of the opposed side beam assemblies, a secondfoot actuated retraction mechanism operatively coupled to the secondretractable side stop, and an auxiliary retraction mechanism including arotatable linkage that extends axially through the framework, and adistal end of the rotatable linkage being coupled to the first footactuated retraction mechanism and to the second foot actuated retractionmechanism. In some embodiments, rotating the auxiliary retractionmechanism in a first rotational direction selectively actuates the firstfoot actuated retraction mechanism to retract the first retractable sidestop without retracting the second retractable side stop, while rotatingthe auxiliary retraction mechanism in a second rotational directionselectively actuates the second foot actuated retraction mechanism toretract the second retractable side stop without retracting the firstretractable side stop, the second rotational direction being oppositethe first rotational direction.

In some embodiments, the first foot actuated retraction mechanismincludes a first rotation linkage assembly coupled to the firstretractable side stop for actuation of the first retractable side stop,a first lineal linkage assembly coupled to and configured to rotate thefirst rotation linkage assembly, the first lineal linkage extendinglaterally through the framework, and a first foot pad coupled to thefirst lineal linkage for translating the first lineal linkage to rotatethe first rotation linkage assembly and actuate the first retractableside stop, the first foot pad being accessible from a second of theopposed side beam assemblies. In some embodiments, the second footactuated retraction mechanism includes a second rotation linkageassembly coupled to the second retractable side stop for actuation ofthe second retractable side stop, a second lineal linkage assemblycoupled to and configured to rotate the second rotation linkageassembly, the second lineal linkage extending laterally through theframework, and a second foot pad coupled to the second lineal linkagefor translating the second lineal linkage to rotate the second rotationlinkage assembly and actuate the second retractable side stop, thesecond foot pad being accessible from the first of the opposed side beamassemblies.

In some embodiments of the disclosure, a first torque return spring isdirectly attached to the first foot actuated retraction mechanism, and asecond torque return spring directly attached to the second footactuated retraction mechanism, the first torque return spring and thesecond torque return spring being configured to resist dynamic loads onthe first foot actuated retraction mechanism and the second footactuated retraction mechanism, respectively. In some embodiments, afirst torque return spring directly attached to the first rotationlinkage assembly, the first torque return spring being configured toresist dynamic loads on the first foot actuated retraction mechanism.The first torque return spring may be a linear spring having a first endattached to the first rotational linkage and a second end attached tothe framework to apply a linear tangential torsion force to the firstrotational linkage.

In some embodiments, the auxiliary retraction mechanism is handactuated, a proximal end of the rotatable linkage being coupled to anactuation handle, and a distal end of the rotatable linkage is coupledto the first lineal linkage assembly and the second lineal linkageassembly. The auxiliary retraction mechanism may include an actuationplate that extends from the rotatable linkage, a first contact structurecoupled to the first lineal linkage assembly and disposed adjacent afirst side of the actuation plate, and a second contact structurecoupled to the second lineal linkage assembly and disposed adjacent asecond side of the actuation plate, the second side of the actuationplate being opposite the first side of the actuation plate. In someembodiments, rotation of the rotatable linkage in the first rotationaldirection causes the actuation plate to engage the first contactstructure and actuate the first rotation linkage assembly for retractionof the first retractable stop, and rotation of the rotatable linkage inthe second rotational direction causes the actuation plate to engage thesecond contact structure and actuate the second rotation linkageassembly for retraction of the second retractable stop.

Various embodiments of a high capacity cargo/container dolly include aframework including an outer frame and a plurality of stringers thatextend parallel to each other and are supported by a forward beamassembly and a rearward beam assembly of the outer frame, the frameworkdefining an upper registration surface, a plurality of tineways attachedto the upper registration surface of the framework, each of theplurality of tineways extending parallel to each other and beingsupported by opposed side beam assemblies and the plurality of stringersof the framework, the tineways extending orthogonal to the opposed sidebeam assemblies, and a plurality of deck modules configured to mount tothe upper registration surface of the framework. Each of the deckmodules may include a lower base plate, an upper tread plate thatextends over the lower base plate, and a plurality of swivel rollersmounted to the lower base plate, each of the plurality of swivel rollersincluding a roller that extends through the upper tread plate. Thetineways and the framework may define a plurality of openings at theupper registration surface, the lower base plates of the plurality ofdeck modules being configured to cover the plurality of openings toshield the upper tread plates of the plurality of deck modules and theplurality of swivel rollers from road spray. In some embodiments, highcapacity cargo/container dolly includes a plurality of self-lockingroller assemblies, each being mounted proximate an edge portion of arespective one of the plurality of deck modules having the edge portionregistered on the upper registration surface of one of the opposing sidebeam assemblies. The upper registration surface may be planar.

Various embodiments of a high capacity cargo/container dolly include anactuation linkage defining a rocker axis and having pivotal coupling tothe high capacity cargo/container dolly about the rocker axis, theactuation linkage including: a first arm that extends in a first lateraldirection from the rocker axis, the first arm being coupled to theplunger assembly of the retractable side stop; a second arm that extendsin a second lateral direction from the rocker axis, the second lateraldirection being generally opposite the first lateral direction; and acounterweight affixed to the second arm. The counterweight and thesecond arm may be unitary. The counterweight and the second arm may alsobe tailored to counter dynamic system inertial moments about the rockeraxis. In some embodiments, a foot actuated retraction mechanismoperatively coupled to the retractable side stop for reconfiguration ofthe retractable side stop from a deployed configuration to a retractedconfiguration, the foot actuated retraction mechanism including arotatable shaft that is rotatable about a rotation axis, wherein theactuation linkage is pivotally mounted to the rotatable shaft for thepivotal coupling to the high capacity cargo/container dolly, the rockeraxis of the actuation linkage being concentric with the rotation axis ofthe rotatable shaft. In some embodiments, the foot actuated retractionmechanism includes a cam arm mounted to and in fixed rotational relationwith the rotatable shaft, the cam arm configured to exert a force on theactuation linkage when the foot actuated retraction mechanism isactuated.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is an upper perspective view of a high capacity cargo/containerdolly according to an embodiment of the disclosure;

FIG. 2 is a lower perspective view of the high capacity cargo/containerdolly of FIG. 1 according to an embodiment of the disclosure;

FIG. 2A is partial, enlarged view of FIG. 2 according to an embodimentof the disclosure;

FIG. 3 is a lower perspective view of a forward axle assembly with anAckerman steering mechanism according to embodiments of the disclosure;

FIG. 4 is an upper perspective view of the forward axle assembly of FIG.3 according to an embodiment of the disclosure;

FIG. 5 is a plan view of the forward axle assembly of FIG. 3 accordingto an embodiment of the disclosure;

FIG. 6 is a lower perspective view of a brake assembly as installed onthe high capacity cargo/container dolly of FIG. 1 according to anembodiment of the disclosure;

FIG. 7 is an enlarged, inset view of an articulating joint of FIG. 6according to an embodiment of the disclosure;

FIG. 8 is a front perspective view of a retractable side stop accordingto an embodiment of the disclosure;

FIG. 9 is a front perspective view of the internal components of theretractable side stop of FIG. 8 according to an embodiment of thedisclosure;

FIG. 10 is a rear perspective view of the internal components of theretractable side stop of FIG. 8 according to an embodiment of thedisclosure;

FIG. 11 is a sectional view of the retractable side stop of FIG. 8coupled to an actuation linkage according to an embodiment of thedisclosure;

FIG. 12 is a front perspective view of internal components of aretractable side stop of according to an embodiment of the disclosure;

FIG. 13 is an elevational view of the internal components of theretractable side stop of FIG. 12 according to an embodiment of thedisclosure;

FIG. 14 is an enlarged, partial elevational view of the retractable sidestop of FIG. 8 installed on the high capacity cargo/container dolly ofFIG. 1 according to an embodiment of the disclosure;

FIG. 15 is a sectional view of the retractable side stop of FIG. 8 in adeployed configuration according to an embodiment of the disclosure;

FIG. 16 is a sectional view of the retractable side stop in FIG. 15 in apartially retracted and released configuration according to anembodiment of the disclosure;

FIG. 16A is an isolated view of select components of FIG. 16 depicting aminimum downward vertical displacement requirement to attain a releaseconfiguration according to an embodiment of the disclosure;

FIG. 16B is an isolated view of the components of FIG. 16A modified toprovide a greater minimum downward vertical displacement to attain therelease configuration according to an embodiment of the disclosure;

FIG. 17 is sectional view of the retractable side stop in FIG. 15 in afully retracted configuration according to an embodiment of thedisclosure;

FIGS. 18 through 20 are sectional views depicting the operation of anactuation member of the retractable side stop of FIG. 8 according to anembodiment of the disclosure;

FIGS. 21 through 23 are partial sectional views depicting the operationof an actuation member of the retractable side stop of FIG. 12 accordingto an embodiment of the disclosure;

FIG. 24 is a partial sectional view of a conventional retractable sidestop experiencing a hang-up malfunction;

FIG. 25 is a partial sectional view of a conventional retractable sidestop experiencing a hold-up malfunction;

FIGS. 26 through 28 are partial sectional views of the retractable sidestop of FIG. 12 being actuated by a roller linkage assembly according toan embodiment of the disclosure;

FIG. 29 is an isolated, upper perspective view of a retraction mechanismassembly coupled to a plurality of retractable side stops according toan embodiment of the disclosure;

FIGS. 30 and 31 are enlarged, partial views of the retraction mechanismassembly of FIG. 29 according to an embodiment of the disclosure;

FIG. 31A is a partial view of the retraction mechanism of FIG. 31modified to include a counterbalance weight to counter dynamic loadsaccording to an embodiment of the disclosure;

FIGS. 32A through 32C are elevational views depicting operation of theretraction mechanism assembly of FIG. 29 according to an embodiment ofthe disclosure;

FIG. 33 is a partial perspective view of an auxiliary retractionmechanism of the retraction mechanism assembly of FIG. 29 according toan embodiment of the disclosure;

FIG. 34 is a perspective view of a self-locking roller assemblyinstalled on the high capacity cargo/container dolly of FIG. 1 accordingto an embodiment of the disclosure;

FIGS. 35 and 36 are perspective, partial cutaway views of the lockingroller assembly of FIG. 34 in a locked configuration according anembodiment of the disclosure;

FIG. 37 is a front elevational view of the locking roller of FIG. 35according to an embodiment of the disclosure;

FIG. 38 is an exploded view of an actuator assembly implemented in thelocking roller assembly of FIG. 34 according to an embodiment of thedisclosure;

FIGS. 39 and 40 are perspective, assembled views of the actuatorassembly of FIG. 38 in the locked configuration according to anembodiment of the disclosure;

FIGS. 41 and 42 are perspective, partial cutaway views of the lockingroller assembly of FIG. 34 in an unlocked configuration according anembodiment of the disclosure;

FIG. 43 is a front elevational view of the locking roller of FIG. 41according to an embodiment of the disclosure;

FIG. 43A is an enlarged, partial view of FIG. 43 ;

FIGS. 44 and 45 are perspective, assembled views of the actuatorassembly of FIG. 38 in the unlocked configuration according to anembodiment of the disclosure;

FIG. 46 is an exploded upper perspective view of the framework and deckmodules of the cargo/container dolly of FIG. 1 according to anembodiment of the disclosure;

FIG. 47 is an enlarged view of the deck modules of FIG. 46 according toan embodiment of the disclosure;

FIG. 48 is a lower perspective view of the deck modules of FIG. 47according to an embodiment of the disclosure; and

FIG. 49 is an exploded view of a deck module of FIG. 47 according to anembodiment of the disclosure.

DETAILED DESCRIPTION

Referring to FIGS. 1 and 2 , a high capacity cargo/container dolly 30 isdepicted according to an embodiment of the disclosure. The high capacitycargo/container dolly 30 includes a framework 32 having an outer frame34 with a forward beam assembly 36 and a rearward beam assembly 38separated by side beam assemblies 42 a and 42 b. A directional Cartesiancoordinate 80 of arbitrary origin is associated with the high capacitycargo/container dolly 30. The side beam assemblies 42 a, 42 b arereferred to collectively and generically by reference character 42. Theframework 32 is supported by forward and rearward wheel and axleassemblies 44, 46. In some embodiments, the forward wheel and axleassembly 44 includes an Ackerman steering mechanism 60 coupled to a towbar 62 that extends forward of the forward beam assembly 36 and rotatesupward (i.e., in the positive z-direction of the Cartesian coordinate 80of FIG. 1 ) to actuate a brake assembly 64. In some embodiments,self-locking roller assemblies 66 are positioned over the side beamassemblies 42. Also, retractable side stops 68 may be positionedproximate the side beam assemblies 42, the retractable side stops 68being actuated by a retraction mechanism assembly 72. A plurality oftineways 74 are supported by and extend laterally (i.e., parallel to they-axis of the Cartesian coordinate 80 of FIG. 1 ) between the side beamassemblies 42. In some embodiments, the framework 32 also supportsroller deck 75 comprising a plurality of deck modules 76, which mayinclude the self-locking roller assemblies 66.

The framework 32 defines a centerline 90 that is parallel to the x-axisof the Cartesian coordinate 80, the centerline 90 extending from theforward beam assembly 36 to the rearward beam assembly 38, and beingequidistant between the side beam assemblies 42. The framework 32 mayinclude stringers 92 that extend between and are supported by theforward and rearward beam assemblies 36, 38, and may be buttressed bygusset beams 94 and gusset plates 96. In some embodiments, the tineways74 extend parallel to each other and are supported by the opposed sidebeam assemblies 42 and the stringers 92 of the framework 32, with thetineways 74 extending orthogonal to the opposed side beam assemblies 42.The framework 32 may include cross members 98 that extend between andare supported by the side beam assemblies 42 and the stringers 92.

Referring to FIGS. 3 through 5 , the forward wheel and axle assembly 44with Ackerman steering mechanism 60 is depicted in isolation accordingto an embodiment of the disclosure. The forward wheel and axle assembly44 includes an axle tube 122 with wheel assemblies 124 coupled toopposed ends 126, 128 of the axle tube 122, with treaded tires 132mounted to the wheel assemblies. The Ackerman steering mechanism 60includes pivoting wheel mounts 134 mounted to the opposed ends 126, 128,by which the wheel assemblies 124 are coupled to the opposed ends 126,128. Each of the pivoting wheel mounts 134 define a wheel assembly pivotaxis 136 about which the respective wheel assembly 124 pivots. TheAckerman steering mechanism 60 further includes steering arms 138, apair of tie rods 142, and a yoke assembly 150. Each of the steering arms138 extend in a direction that is substantially parallel to a directionof travel 144 of the respective wheel assembly 124 and includes asteering arm pivot 146 to which the tie rods 142 are mounted. Eachsteering arm pivot 146 defines a steering arm pivot axis 148 thatextends vertically (i.e., parallel to the z-axis of the Cartesiancoordinate 80 of FIG. 1 ). The yoke assembly 150 is mounted to the axletube 122 about a pivot 152, the pivot 152 defining a yoke pivot axis 154that extends vertically. The tie rods 142 are mounted to the yokeassembly 150 via a pair of tie rod pivots 156, each defining a linkagepivot axis 158 that extends vertically. The linkage pivot axes 158 areaxially and laterally spaced relative to the yoke pivot axis 154. Insome embodiments, the yoke assembly 150 extends through a slot 162defined in the forward beam assembly 36 (FIG. 1 ) and may includelaterally extending bosses 164 for pivotal mounting of the tow bar 62.The yoke assembly 150 may include a hanger 166 and a spring plate 168that extend downward (i.e., in the negative z-direction of the Cartesiancoordinate 80 of FIG. 1 ) for facilitating the brake assembly 64. Theyoke assembly 150 may include a brake latch plate 172 to facilitatelatching of the tow bar 62.

The linkage pivot axes 158 and the steering arm pivot axes 148 arelocated on the same side of the yoke pivot axis 154 and the wheelassembly pivot axes 136 in the axial direction, the axial directionbeing parallel to the z-axis of the Cartesian coordinate 80 (FIG. 1 ) ofthe high capacity cargo/container dolly 30. For example, FIGS. 3 through5 depict the linkage pivot axes 158 as being rearward (i.e., in thenegative x-direction of the Cartesian coordinate 80 of FIG. 1 ) of theyoke pivot axis 154 and the steering arm pivot axes 148 as beingrearward of the wheel assembly pivot axes 136. Alternatively, thisarrangement may be reversed. That is, the linkage pivot axes 158 may bedefined forward (i.e., in the positive x-direction of the Cartesiancoordinate 80 of FIG. 1 ) of the yoke pivot axis 154 and the steeringarm pivot axes 148 forward of the wheel assembly pivot axes 136.

The lateral displacements of the linkage pivot axes 158 relative to theyoke pivot axis 154 provide the angled steering arm characteristic ofthe Ackerman steering geometry, thereby providing the effect of theinside wheel defining a smaller turn radius that the outside wheel whenthe cargo/container dolly 30 turns. Connecting lines 174 between theyoke pivot axis 154 and the linkage pivot axes 158, depicted in phantomin FIG. 5 , effectively define the canted linkages characteristic ofAckerman steering systems.

Referring to FIGS. 6 and 7 , the brake assembly 64 is depicted ingreater detail according to an embodiment of the disclosure. The brakeassembly 64 includes an actuation train 222 coupled to a brake bar 224.The actuation train 222 passes through the hanger 166 of the yokeassembly 150 and is suspended on a proximate end 226 by an offset pivot227 that depends from the tow bar 62 and on a distal end 228 by thebrake bar 224. The brake bar 224 is suspended by a pair of hangers 230that depend from the framework 32, the hangers 230 being dimensioned toallow the brake bar 224 to slide fore and aft during operation. Thebrake bar 224 may include a pair of brake shoes 232 disposed proximateopposed ends of the brake bar 224, the brake shoes 232 being in axialalignment with the treaded tires 132. In the depicted embodiment, theactuation train 222 is coupled to a bracket 238 that depends from thebrake bar 224, with a release spring 240 operatively coupled between theactuation train 222 and the bracket 238. A compression spring 242 iscoupled on a first end to the actuation train 222 and on a second end tothe spring plate 168 of the yoke assembly 150. In some embodiments, theactuation train 222 includes a forward portion 252 and an aft portion254 that are pivotally connected about a pin 256 that defines anarticulating joint 258 that rotates about a vertical axis 260. Thearticulating joint 258 may be in proximate alignment with the yoke pivotaxis 154 of the yoke pin 152 when the tow bar 62 is in a towing(downward) configuration.

In operation, when the tow bar 62 is rotated upward from the towingconfiguration, the offset pivot 227 pulls the actuation train 222 in aforward direction 262, causing the brake bar 224 to translate forward sothat the brake shoes 232 engage the treaded tires 132, thereby brakingthe high capacity cargo/container dolly 30. The release spring 240 iscompressed against the bracket 238 when the tow bar is lowered to pushthe brake bar 224 and brake shoes 232 rearward, thereby releasing thebrake assembly 64. The release spring 240 enables the aft portion 254 ofthe drive train 222 to slide and move within an oversized passagedefined by the bracket 238 during release, which prevents the drivetrain 222 from binding within the bracket. The bracket 238 with itsoversized passage and the release spring 240 also enables setting andreleasing of the brake assembly 64 when the aft portion 254 passesthrough the bracket 238 at an angle, for example when the forward wheeland axle assembly 44 is in a turning configuration.

The compression spring 242 is sized to be compressed when the tow bar 62is in the towing configuration, thereby applying a biasing force on thetow bar 62 that suspends the tow bar 62 above the ground and may alsoassist personnel with lifting the tow bar 62 into the brakingconfiguration. The brake bar 224 and brake shoes 232 remain in thebraking configuration as long as the tow bar 62 is upright. The tow bar62 may include a latch 264 that engages the brake latch plate 172 of theyoke assembly 150, thereby maintaining the tow bar 62 in the uprightposition and the brake shoes 232 in contact with the treaded tires 132.The depicted embodiment portrays the brake assembly 64 as engaging theforward wheel and axle assembly 44. Alternatively or in addition, it iscontemplated that the brake assembly 64 engage the rearward wheel andaxle assembly 46 (FIG. 2 ) by moving or replicating the arrangement ofthe brake bar 224, brake shoes 232, bracket 238, and hangers 230 behindthe rearward wheel and axle assembly 46 and extending the aft portion254 to reach behind the rearward wheel and axle assembly 46.

The articulating joint 258 enables the actuation train 222 to conform tothe yoke assembly 150 during steering of the high capacitycargo/container dolly 30. The hanger 166 of the yoke assembly 150 actsas a guide that causes the forward portion 252 of the actuation train222 to rotate laterally with the yoke assembly 150. The articulatedjoint 258, being in proximate alignment with the yoke pivot axis 154,enables the aft portion 254 of the actuation train 222 to remainsubstantially aligned in the forward direction 262 during a turn. Thecoupling between the bracket 238 and the aft portion 254 includesufficient play to accommodate some misalignment of the aft portion 254relative to the forward direction 262. For example, a passage in thebracket 238 through which the aft portion 254 passes may be oversizedrelative to a local diameter of the aft portion 254. The articulatedjoint 258 may also enable the brake assembly 64 to be actuated when theAckerman steering mechanism 60 of the high capacity cargo/containerdolly 30 is in a turning configuration. In some embodiments, the rangeof rotation of the yoke assembly 150, as defined by the slot 162 of theforward beam assembly 36, may be sufficiently limited to enable suchactuation.

Referring to FIGS. 8 through 13 , embodiments of the retractable sidestop 68 are depicted in greater detail according to embodiments of thedisclosure. Herein, embodiments of the retractable side stops 68 arereferred to collectively or generically by reference character 68, withspecific embodiments being referred to by reference character 68followed by a letter suffix (e.g., retractable side stop 68 a).Retractable side stop 68 a is depicted in FIGS. 8 through 11 , andretractable side stop 68 b is depicted in FIGS. 12 and 13 . It isunderstood that retractable side stops 68 a and 68 b share many of thesame components and attributes, which are indicated with same-numberedreference characters, and that aspects of each may be combined with theother.

The retractable side stops 68 include a housing 302 that surrounds aplunger assembly 304 and a roller linkage assembly 306. In someembodiments, a stop bracket 308 is attached to the housing 302. In FIGS.8 through 13 , the retractable side stop 68 and plunger assembly 304 aredepicted in a deployed configuration 310. The housing 302 includes oneor more side walls 312 having a top end 314 and a bottom end 316. Thehousing 302 may further include a base 318 that depends from the bottomend 316. In some embodiments, the stop bracket 308 is attached to theside wall 312 and extends over the open top end 314 of the housing 302.The housing 302 may further include a spacer 322 attached to an exteriorsurface 324 of the side wall(s) 312. In the depicted embodiment, thehousing 302 includes a square tubing 326 that presents four side walls312. Other forms are contemplated, such as round tubing (presenting asingle side wall) or other polygonal geometries (presenting more or lessthan four side walls).

In some embodiments, the plunger assembly 304, includes a platformassembly 332, a stop assembly 334, and a catch assembly 336. Theplatform assembly 332 may include tab portions 338 and guide plates 342that depend from a platform portion 344. The stop assembly 334 isattached to and extends upward from the platform portion 344, and mayinclude a pair of stop fingers 346 joined and separated by a lateralspacer 348. The stop fingers 346 include laterally inward faces 347 thatface in a laterally inward direction 358 (i.e., parallel to the y-axisof the Cartesian coordinate 80 of FIG. 1 and toward the centerline 90 ofthe framework 32), the laterally inward faces 347 defining a verticalstop plane 349. The vertical stop plane 349 establishes the locallateral outward limit within which a cargo container is contained on thedolly 30 when the retractable side stops 68 are deployed.

In some embodiments, the catch assembly 336 includes a hook 352 thatincludes a shank portion 354 and a bend portion 356, the bend portion356 extending from the shank portion 354 in the laterally inwarddirection 358. The catch assembly 336 is depicted in a captureconfiguration 350 in FIGS. 8 through 13 , wherein the bend portion 356extends beyond the vertical stop plane 349 in the laterally inwarddirection 358. The hook 352 extends upward from a lever 362, the lever362 being attached to a pivot tube 364. The lever 362 includes alaterally inward portion 361 that extends from the pivot tube 364 in thelaterally inward direction 358, and a laterally outward portion 363 thatextends in a laterally outward direction 365 (i.e., parallel to they-axis of the Cartesian coordinate 80 of FIG. 1 and away from thecenterline 90 of the framework 32) from the pivot tube 364. Thelaterally inward portion 361 of the lever 362 extends underneath thestop bracket 308. The pivot tube 364 pivots about a pin or fastener 366that is supported by and between the stop fingers 346. The catchassembly 336 may include a spring loaded cap assembly 368 coupled to thelever 362, the spring loaded cap assembly 368 and the hook 352 beingcoupled to the lever 362 on opposite sides of the pivot tube 364. Thespring loaded cap assembly 368 includes a top portion 372 and a bottomportion 374 joined together by a spring 376. The top portion 372 isconnected to the lever 362, and the bottom portion 374 is connected tothe platform assembly 332.

The plunger assembly 304 includes a stem 378 that defines a stem axis382, the stem 378 supporting and depending from the platform assembly332. In some embodiments, a return spring 384 is disposed between theplatform assembly 332 and the housing 302. In one non-limiting example,the return spring 384 is a coil spring 386 that is concentric about thestem 378 and is captured by and between the platform portion 344 of theplunger assembly 304 and the base 318 of the housing 302 (depicted). Insome embodiments, a stop 388 is connected to or otherwise formed on thestem 378, the stop 388 being disposed below the housing 302.

In some embodiments, the roller linkage assembly 306 includes a pair ofpivot arms 402 that straddle the stop and catch assemblies 334 and 336.In some embodiments, the pivot arms 402 are joined and separated by aspacer 404 and a pivot passage 406 is defined that passes through thepivot arms 402 and spacer 404. The pivot arms 402 may also be separatedby a gusset 408. The roller linkage assembly 306 is supported by a pivotpin 422 (e.g., a fastener) that passes through the pivot passage 406,the pivot pin 422 being attached to and supported by the housing 302 anddefining a linkage rotation axis 424 about which the roller linkageassembly 306 rotates. In some embodiments, the pivot arms 402 eachinclude a lower roller 432 and an upper roller 434. Each of the rollers432, 434 may be disposed in respective slotted portions 436, 438 andeach being rotatable about an upper roller axis 442 and a lower rolleraxis 444, respectively. The axes 424, 442, and 444 may be parallel toeach other.

The retractable side stop 68 may include an actuator member 450 foractively retracting the roller linkage assembly 306, instead of relyingon a passive gravitational force. For the retractable side stop 68 a,the lateral spacer 348 acts as the actuator member 450, being configuredto interact with the spacer 404, for example by way of an extension tab452 that extends from the spacer 404 in the laterally inward direction358 and into a translation path 453 of the lateral spacer 348 (FIGS. 11and 18-20 ). For the retractable side stop 68 b, the actuator member 450extends laterally beyond at least one of the stop fingers 346 of thestop assembly 334 and over at least one of the pivot arms 402 and may bein the form of, for example, a pin 454 (FIGS. 12 and 13 ). The pivotarm(s) 402 may include a cam surface 456 for engaging the actuation bar454.

A first reference line 446 may be defined that passes through the lowerroller axis 444 and the linkage rotation axis 424. Also, a secondreference line 448 may be defined that passes through the upper rolleraxis 442 and the linkage rotation axis 424. The reference lines 446 and448 are co-planar on a plane that is orthogonal to the linkage rotationaxis 424. A non-zero angle θ may be defined about the linkage rotationaxis 424 between the reference lines 446 and 448. An actuation radius Ris defined from the linkage rotation axis 424 to an extremity 468 of theupper roller 434 along the second reference line 448.

Functionally, the housing 302, the tab portions 338, and the guideplates 342 cooperate to guide the plunger assembly 304 along the stemaxis 382. That is, the lateral faces of the tab portions 338 and theends of the guide plates 342 slide along interior surfaces of thehousing 302 during actuation and return. The spacer 322 of the housing302 is configured for mounting of the retractable side stop 68 to theframework 32. In some embodiments, the base 318 of the housing 302 actsto maintain the return spring 384 in compression. That is, the returnspring 384 may be sized and dimensioned to be in compression between theplatform assembly 332 and the housing 302 when the stop 388 isregistered against the housing 302, thereby exerting an upward returnforce FR on the plunger assembly 304 to extend the roller linkageassembly 306, the stop assembly 334, and the catch assembly 336 at leastpartially above the housing 302. The base 318 and stop 388 may alsocooperate to define an upper limit of the stroke of the plunger assembly304.

The stop fingers 346 act to prevent a cargo container 370 (FIG. 14 )from sliding laterally over the side beam assembly 24 to which theretractable side stop 68 is mounted. The catch assembly 336 captures aflange 371 of the cargo container 370 and prevents the container 370from rising over the retractable side stop 68 during transport. The stopbracket 308 contacts and holds the lever 362 down when the plungerassembly 304 is in the deployed configuration 310. By holding the lever362 down, the catch assembly 336 is maintained in the captureconfiguration 350. The spring loaded cap assembly 368 applies a biasingforce FB that biases the lever 362 upward and away from the platformassembly 332 to rotate the hook 352 in the laterally outward direction365 when the plunger assembly 304 is retracted away from the stopbracket 308. The roller linkage assembly 306 functions to passivelyretract the plunger assembly 304 when a container is slid over theretractable side stop 68 from the outside, as explained below attendantFIGS. 26 through 28 .

Referring to FIGS. 14 through 17 , active, operator-selectable operationof the retractable side stop 68, is depicted according to an embodimentof the disclosure. While retractable side stop 68 a is depicted in FIGS.14 through 17 , the attendant discussion applies to the retractable sidestop 68 b as well. In a fully engaged configuration 470 (FIGS. 14 and 15), the retractable side stop 68 is in the deployed configuration 310,with the catch assembly 336 in the capture configuration 350 to capturethe cargo container 370. In this way, the cargo container 370 isconstrained laterally on the framework 32 and has limited verticalmovement. The bottom of the cargo container 370 rides on a plurality ofswivel casters 472 having upper extremities 474 that are coplanar with aregistration plane 476.

In the deployed configuration 310, the roller linkage assembly 306, thestop assembly 334, and the catch assembly 336 extend upward, through theregistration plane 476. Also, the registration plane 476 intersects thevertical stop plane 349 along an intersection line 477. The intersectionline 477 may be generally parallel to the centerline 90, and representsan extreme corner below and laterally outside of which containers orother cargo generally do not extend.

To release the cargo container 370, a downward axial force FA is exertedon the stem 378, for example with the retraction mechanism assembly 72as described below attendant to FIGS. 29 through 31 . The downward axialforce FA causes the plunger assembly 304 to translate axially downward,relative to and guided by the housing 302. As the plunger assembly 304translates axially downward, the laterally inward portion 361 of thelever 362 pulls away from the stop bracket 308, so that the biasingforce FB exerted by the spring loaded cap assembly 368 rotates the hook352 in the laterally outward direction 365 and into a releaseconfiguration 478 (FIG. 16 ). In the release configuration 478, the bendportion 356 of the hook 352 is rotated in the laterally outwarddirection 365, beyond the vertical stop plane 349 defined by thelaterally inward faces 347 of the stop fingers 346. In some embodiments,the laterally outward rotation of the hook 352 is limited by the lateralspacer 348 of the stop assembly 334, which engages the shank portion 354of the hook 352. In the release configuration 478, because the bendportion 356 of the hook 352 is laterally outward of the vertical stopplane 349, the plunger assembly 304 can continue translating axiallydownward without interference from the cargo container 370.

As the plunger assembly 304 translates axially downward, roller linkageassembly 306, which is mounted to the (stationary) housing 302, rotatesabout the linkage rotation axis 424, primarily due to gravity. Therotation causes the upper rollers 434 to arc along the actuation radiusR and rotate below the registration plane 476 (FIG. 17 ). In someembodiments, the actuation radius R is dimensioned so that the upperrollers 434 rotate below the registration plane 476 before passingthrough the vertical stop plane 349. In this way, the upper rollers 434are assured to pass under and not collide with the cargo container 370during retraction of the retractable side stop 68.

Referring to FIGS. 16A and 16B and again to FIG. 16 , a minimum downwardvertical displacement Δ required to configure the catch assembly 336 inthe release configuration 478 is illustrated according to an embodimentof the disclosure. Here, the hook 352, lever 362, pivot tube 364, and acontacting portion of the stop bracket 308 of the catch assembly 336 ofFIG. 16 is depicted in isolation in FIGS. 16A and 16B. In FIG. 16 , thelaterally inward portion 361 of the lever 362 is still in contact withthe stop bracket 308 as the hook 352 rotates into contact with thelateral spacer 348, such that the catch assembly 336 ceases rotation andundergoes pure axial translation along the stem axis 382 and away fromthe stop bracket 308. That is, FIG. 16 represents minimum downwardvertical displacement Δ of downward axial translation of the plungerassembly 304 required to attain the release configuration 478.

Isolation of the components of FIGS. 16A and 16B depicts how the minimumdownward vertical displacement Δ may be governed by a length of thelaterally inward portion 361 of the lever 362 having a lateral dimensionL in the laterally inward direction 358. Herein, the “lateral dimension”is a dimension of a length parallel to the lateral direction (i.e.,parallel to the y-axis of Cartesian coordinate 80 of FIG. 1 ). A firstlateral dimension L1 for the laterally inward portion 361 results in afirst required minimum downward vertical displacement Δ1, while a secondlateral dimension L2 results in a second required minimum downwardvertical displacement Δ2. The required minimum downward verticaldisplacement Δ is directly proportional to the lateral dimension L ofthe laterally inward portion 361 of the lever 362. In the illustrationsof FIGS. 16A and 16B, lateral dimension L2 is greater than lateraldimension L1, so that the required minimum downward verticaldisplacement Δ2 is greater than the required minimum downward verticaldisplacement Δ1. A rotation angle α is determined by the interaction ofthe hook 352 with the lateral spacer 348 and is the same regardless ofthe lateral dimension L of the laterally inward portion 361.

Heretofore, conventional designs of retractable side stops typicallyfocus on quick release of cargo containers (i.e., short minimum downwardvertical displacements Δ). Advantages of a quick release include a smallamount of stroke for the plunger assembly 304 to attain the releaseconfiguration, as well as a shorter clearance requirement between theflange 371 of the cargo container 370 and the bend portion 356 of thehook 352 (FIG. 14 ). Accordingly, conventional designs are typicallyconfigured to provide a minimum downward vertical displacement Δ on theorder of 6 to 10 millimeters (about ¼- to ⅜-inches).

We have found, however, that short minimum downward verticaldisplacements are prone to inadvertent release during the rigors oftransport. Jostling and jolting of cargo dollies over uneven terrain orwhen encountering low clearance obstacles can cause dynamic loads thatin turn cause the plunger assemblies of conventional retractable sidestops to deflect enough to cause the catch assemblies to momentarilyrelease. Such spurious release occurs at an instant in time when thecatch assemblies are needed most to contain the cargo. As a result, thecargo can inadvertently become unmoored from the cargo dolly duringtransport.

As a remedy, some embodiments of the disclosure are configured with thelateral dimension L of the laterally inward portion 361 of the lever 362of the catch assembly 336 to provide the minimum downward verticaldisplacement Δ that is in a range of 15 to 38 millimeters (i.e., ⅝- to1½-inches) inclusive. In some embodiments, the minimum downward verticaldisplacement Δ is in a range of 18 to 25 millimeters (i.e., ¾- to1-inches) inclusive. Herein, a range that is said to be “inclusive”includes the endpoint values of the range as well as all values betweenthe endpoints. We have found, after rigorous testing, that retention ofcargo containers 370 when using retractable side stops 68 designed withminimum downward vertical displacements Δ that fall within these rangesis significantly improved over conventional quick release retractableside stops.

Referring to FIGS. 18 through 20 , operation of the actuator 450 ofretractable side stop 68 a for active rotation of the roller linkageassembly 306 below the registration plane 476 is depicted according toan embodiment of the disclosure. The extension tab 452 extends from thespacer 404 of the roller linkage assembly 306 in the laterally inwarddirection 358 and into the translation path 453 of the actuation member450 (e.g., the lateral spacer 348 of the stop assembly 334). If thegravitational force is inadequate to cause the roller linkage assembly306 to rotate below the registration plane 476, the actuation member 450(lateral spacer 348) can collide with the extension tab 452 whentranslated along the translation path 453 during the retraction of theplunger assembly 304 (FIG. 18 ). The collision forces the roller linkageassembly 306 to rotate about the rotation axis 424 of the pivot pin 422(FIG. 19 ). In the event that gravitational forces are inadequate toovercome the static friction between the pivot pin 422 and the pivotpassage 406, the collision and forced rotation overcomes the staticfriction, enabling the roller linkage assembly 306 to complete itsrotation under the influence of gravity (FIG. 20 ).

Referring to FIGS. 21 through 23 , operation of the actuator 450, 454 ofretractable side stop 68 b for active rotation of the roller linkageassembly 306 below the registration plane 476 is depicted according toan embodiment of the disclosure. Because the actuation member 450 (e.g.,the actuation bar or pin 454) extends laterally beyond the vertical stopplane 349, the actuation member 450 (pin 454) can engage the pivotarm(s) 402 if the gravitational force is inadequate to rotate the rollerlinkage assembly 306 downward, forcing the roller linkage assembly 306to rotate about the rotation axis 424 of the pivot pin 422. Theactuation member 450, 454 may slide along the pivot arm(s) 402 (e.g.,along the cam surface 456) at least until the upper roller 434 isactively positioned below the registration plane 476. The cam surface456 may be recessed to assure that the rotation of the pivot arms 402lag or follow the downward axial translation of the plunger assembly304. In this way, the actuation pin 454 doesn't force the pivot arms 402against the platform portion 344 during the downward axial translationof the plunger assembly 304, thereby preventing undue stresses on theactuation pin 454, the pivot arms 402, and the retractable side stop 68b generally.

Accordingly, a retracted configuration 479 of the retractable side stop68 is defined when the stop assembly 334 and the catch assembly 336 aretranslated below the registration plane 476, and the roller linkageassembly 306 is rotated below the registration plane 476 (e.g., FIGS. 20and 23 ). In the retracted configuration 479, the cargo container 370can be rolled off the high capacity cargo/container dolly 30 withoutinterference from the retractable side stop 68.

Referring to FIGS. 24 and 25 , the advantages of the retractable sidestop 68 in reference to a conventional retractable side stop 480 isexplained. The conventional retractable side stop 480 includes aconventional roller linkage assembly 482 that rotates about a pivot pin484. The conventional retractable side stop 480 relies solely on passivegravitational forces to rotate the conventional roller linkage assembly482 below the registration plane 476, and thus relies on a low frictioninterface 486 between the pivot pin 484 and the roller linkage assembly482. Over time, the friction may increase, for example due to corrosionor the lodging of debris at the interface 486. This can cause theconventional roller linkage assembly 482 to “hang up,” i.e., not rotatecompletely below the registration plane 476 (FIG. 24 ). If there is sucha hang up, the conventional roller linkage assembly 482 may interferewith the offloading of the cargo container 370 over the conventionalretractable side stop 480. By actively rotating the roller linkageassembly 306 of the retractable side stop 68, the hazard of linkageassembly hang up is reduced or eliminated.

Also, the conventional roller linkage assembly 482 of the conventionalretractable side stop 480 often has an upper extremity 488 that definesa conventional actuation radius R′ that arcs through the vertical stopplane 349 above the registration plane 476. Accordingly, if the cargocontainer 370 is at or proximate the vertical stop plane 349 when theconventional retractable side stop 480 is retracted, the conventionalroller linkage assembly 482 can rotate into and be “held up” by thecargo container 370 (FIG. 25 ). In such a scenario, the conventionalroller linkage assembly 482 may also interfere with the offloading ofthe cargo container 370 over the conventional retractable side stop 480.By sizing the pivot arms 402 of the roller linkage assembly 306 so thatthe actuation radius R does not swing through the vertical stop plane349 above the registration plane 476 (FIG. 17 ), the roller linkageassembly 306 cannot be held up by the cargo container 370, therebymitigating this hazard.

Referring to FIGS. 26 through 28 , the function of the roller linkageassembly 306 is depicted according to embodiments of the disclosure.While FIGS. 26 through 28 depict the retractable side stop 68 b, thediscussed aspects of the roller linkage assembly 306 also appliesgenerally to the retractable side stop 68 a, except where specificallynoted. When an object 498 such as a cargo container approaches theretractable side stop 68 along the registration plane 476 and in thelaterally inward direction 358 from the outside of the high capacitycargo/container dolly 30, the object 498 first encounters the upperroller 434 of the roller linkage assembly 306 (FIG. 2.6 ). As the object498 slides over the retractable side stop 68, a lateral force FL exertedon the upper roller 434 causes the roller linkage assembly 306 to rotateabout the rotation axis 424 of the pivot pin 422. The rotation of theroller linkage assembly 306 causes a downward force FD to be exerted onthe platform assembly 332 of the plunger assembly 304, therebyovercoming the upward return force FR exerted on the plunger assembly304 by the return spring 384. The downward force FD causes the plungerassembly 304 to retract within the housing 302, with the attendantdownward axial translation of the stop assembly 334 (FIG. 27 ) and thecatch assembly 336. In some embodiments, the lower roller 432 rollsalong the platform portion 344 of the platform assembly 332 tofacilitate a low friction coupling between the roller linkage assembly306 and the platform assembly 332 as the plunger assembly 304 is pusheddownward by the roller linkage assembly 306. For the retractable sidestop 68 b, the recess of the cam surface 456 may prevent collisionbetween the actuation member 450 and the pivot arm(s) 402 of the rollerlinkage assembly 306 during the actuation of the plunger assembly 304 bythe roller linkage assembly 306. As the object 498 progresses over theretractable side stop 68, the stop assembly 334 and the catch assembly336 are fully retracted below the registration plane 476, enablingunimpeded passage of the object 498 over the retractable side stop 68(FIG. 28 ).

Referring to FIGS. 29 through 31 , the retraction mechanism assembly 72for active, operator-selected operation of the retractable side stops 68is depicted in greater detail according to an embodiment of thedisclosure. The retraction mechanism assembly 72 includes two footactuated retraction mechanisms 502 a and 502 b, each coupled to at leastone respective retractable side stop 68. The foot actuated retractionmechanisms 502 a, 502 b are referred to collectively or generically withreference character 502. The foot actuated retraction mechanisms 502 areaccessible from opposing side beam assemblies 42. That is, the footactuated retraction mechanism 502 a is accessible from side beamassembly 42 a to retract retractable side stop(s) 68 that are mounted toor proximate side beam assembly 42 b, and the foot actuated retractionmechanism 502 b is accessible from side beam assembly 42 b to retractretractable side stop(s) 68 that are mounted to or proximate side beamassembly 42 a (FIG. 2 ). The foot actuated retraction mechanisms 502 maypass through one or more structural tubes 506 depicted in phantom inFIGS. 29 through 30 . In some embodiments, an auxiliary retractionmechanism 504 extends axially, substantially perpendicular to the footactuated retraction mechanisms 502. In some embodiments, the auxiliaryretraction mechanism 504 is hand actuated.

Each foot actuated retraction mechanism 502 includes a rotation linkageassembly 512, a lineal linkage assembly 514, and an actuation pedalassembly 516. Each rotation linkage assembly 512 includes a rotatableshaft 522 suspended by pillow blocks 524 and bi-directionally rotatableabout a rotation axis 526. The rotatable shaft 522 may include sectionsof rod and tube held together by fasteners 528. In some embodiments, camarms 532 are mounted to and in fixed relation with the rotatable shaft522. The cam arms 532 may include a radially extending member 534 with acam rod 536 that extends perpendicular thereto. In some embodiments, anactuation linkage 540 is mounted to the rotatable shaft 522, theactuation linkage 540 including a collar 542, an arm 544 such as a baror rod extending from the collar 542, and a coupler 546 (such as thedepicted chain link) affixed to and between the arm 544 and plungerassembly 304. The collar 542 defines a rocker axis 550 that isconcentric with the rotation axis 526 of the rotatable shaft 52 andabout which the collar 542 and arm 544 rotate. The collar 542 is sizedto enable the rotatable shaft 522 to rotate freely therein. In someembodiments, the collar 542 includes a grease zerk fitting 548 forfacilitating lubrication of the collar 542 about the rotatable shaft522. In some embodiments, an offset pivot 552 extends from the rotatableshaft 522.

In some embodiments, the lineal linkage assembly 514 includes a rod 562having a proximal yoke 564 and a distal yoke 566 coupled to opposingends thereof. The proximal yoke 564 is pivotally coupled to theactuation pedal assembly 516, and the distal yoke 566 is pivotallymounted to the offset 552 of the rotation linkage assembly 512. Theactuation pedal assembly 516 may include a foot pad 572 attached to alever arm 574, the lever arm 574 being mounted to a pivot tube 576 andincluding an offset pivot 578 that extends from the pivot tube 576. Insome embodiments, the pivot tube 576 rotates about a support 582 (e.g.,a fastener) that is mounted to the framework 32. The pivot tube 576 mayinclude a grease zerk fitting 584 for lubricating the pivot tube 576about the support 582.

In some embodiments, the actuation pedal assembly 516 is accessiblethrough the sides of the side beam assemblies 42. An access notch 592 isformed in each side beam assembly 42 and a reinforcement housing 594fitted and welded into the notch 592 (FIG. 1 ). Similarly, the stringersmay also be formed with notches 596 and the structural tubes 506 weldedinto the notches 596 (FIG. 2 ).

In some embodiments, a torque return spring 598 is coupled to therotatable shaft 522 in a manner that applies a biasing torsion BT to therotatable shaft 522 (FIG. 2A). The biasing torsion BT acts to apply atorque that helps maintain the rotatable shaft 522 in a non-actuatedorientation (i.e., foot pad 572 and lever arm 574 in an elevatedorientation within the reinforcement housing 594). In the depictedembodiment, the torque return spring 598 is coupled on one end to thebottom of one of the fasteners 528 (FIG. 2A) and to a panel fastener 597on the other end to apply a tangential linear torsion force FT (FIGS. 2Aand 30 ) in the laterally outward direction 365 to effect the biasingtorsion BT about the rotation axis 526. The torque return spring 598 maybe fitted with anchor tabs 599 to secure the return spring 598 to thefasteners 528, 597. While the depicted embodiment presents a linearspring applying a tangential linear torsion force FT to the rotatableshaft 522 to generate the biasing torsion BT, other forms of generatingthe biasing torsion BT on the rotatable shaft 522 are contemplated,including a torsion spring concentric about the rotation axis 526 orabout a rotation axis of the pivot tube 576.

Referring to FIG. 31A, a rotation linkage assembly 512 a having acounterbalanced actuation linkage 540 a is depicted according anembodiment of the disclosure. The rotation linkage assembly 512 a andactuation linkage 540 a include many of the same components andattributes as the rotation linkage assembly 512 and actuation linkage540, which are indicated with same-numbered reference characters. Theactuation linkage 540 a includes the first arm 544 affixed to the collar542 and extending in the laterally outward direction 365 from the rockeraxis 550, as well as a second arm 554 affixed to the collar 542 thatextends in the laterally inward direction 358 from the rocker axis 550to a free end 555. Accordingly, the first and second arms 544 and 554extend in generally opposing lateral directions. The first arm 544 iscoupled to the plunger assembly 304 with the coupler 546 (such as thedepicted chain link). A counterweight 556 is affixed to the second arm554 at the free end 555 in some embodiments, the second arm 554 and thecounterweight 556 are unitary.

Functionally, the counterbalanced actuation linkage 540 a preventsspurious release of the retractable side stops 68 when the high capacitycargo/container dolly 30 is in transit. The counterweight 556 and thesecond arm 554 may be tailored to counter dynamic loads exerted on theplunger assembly 304 during impact loads generated by verticaldisplacements as the high capacity cargo/container dolly 30 travels overuneven terrain or when encountering low clearance obstacles. Suchdynamic loads include the inertial or momentum forces of the retractablecomponents within the retractable side stops 68 (e.g., the plungerassembly 304 and, to some extent, the roller linkage assembly 306) aswell as the inertial moments generated by the rotation linkage assembly512 a and actuation pedal assembly 516 which are exerted on the plungerassembly 304 via the rotation linkage assembly 512 a. These inertialforces generate a system inertial moment M1 about the rocker axis 550(depicted clockwise in FIG. 31A). Simultaneously, the same displacementscause the second arm 554 and the counterweight 556 to generate acountering inertial moment M2 about the rocker axis 550 (depictedcounterclockwise in FIG. 31A) that counters the system inertial momentM1. The counterweight 556 and the second arm 554 may be sized anddimensioned so that the countering inertial moment M2 substantially orcompletely cancels the system inertial moment M1, thereby preventing thedynamic load from retracting and releasing the retractable side stop 68.

Referring to FIGS. 32A through 32C, operation of the retractionmechanism assembly 72 is depicted according to an embodiment of thedisclosure. An operator inserts a foot into the access notch 592 (FIG.32A) and depresses the actuation pedal assembly 516 by pushing down onthe foot pad 572 with the foot (FIG. 32B). This causes the offset pivot578 to rotate in the laterally outward direction 365, thereby laterallytranslating the lineal linkage assembly 514 toward the operator and awayfrom the rotation linkage assembly 512. The lateral translation of thelineal linkage assembly 514 pulls on the offset 552 of the rotationlinkage assembly 512, causing the rotation linkage assembly 512 torotate about the rotation axis 526, which causes the cam arms 532 torotate and the cam rods 536 to bear down on and exert a force on theactuation linkage 540. The collars 542 of the actuation linkages 540rotate downward about the rotatable shaft 522 to translate the plungerassemblies 304 of the retractable side stops 68 downward and retract theretractable side stops 68.

Functionally, the foot actuated retraction mechanisms 502 enablepersonnel to retract retractable side stops 68 from an opposite side ofthe dolly 30. This enables the personnel to retract the side stops 68with the foot pad 572 and push a pallet or cargo container 370 over theretracted stops 68 from the opposite side of the high capacitycargo/container dolly 30 while the foot pad 572 is depressed (FIG. 32B).When the foot pad 572 is released, the return spring 384 of theretractable side stops 68 cause the upper rollers 434 of the rollerlinkage assemblies 306 to engage the bottom surface of the cargocontainer, maintaining the retractable side stops 68 in the retractedconfiguration 479 while enabling the cargo container to roll freely overthe retractable side stops 68. Accordingly, operating personnel needonly depress the foot pad 572 initially, until the cargo container ispushed over the retractable side stop 68. There is no need to hold downthe foot pad 572 thereafter, enabling operating personnel to step awayfrom the foot pad 572 as they push the cargo container off the highcapacity cargo/container dolly 30 (FIG. 32C).

The torque return spring 598 may assist in returning the foot pad 572 tothe unactuated orientation. However, the primary purpose of the torquereturn spring 598 is to resist or counter dynamic loads on the plungerassembly 304 during transport of the high capacity cargo/container dolly30. The spring 598 acts on the rotation linkage assembly which in turnacts on the plunger assembly 304. The rotation linkage assembly 512includes several components that impose a moment on the rotatable shaft522 toward actuation. Those components include the foot pad 572, leverarm 574, and cam arms 532, all of which extend laterally outward fromthe rotatable shaft 522. Under a dynamic load (e.g., jostling or joltingwhile being transported over uneven terrain or obstacles), we found thatthe inertia generated by these components can actually cause theretractable side stops 68 to retract. The biasing torsion BT helpsmaintain the retractable side stops 68 in the deployed configuration310.

By disposing the actuation pedal assembly 516 in the access notch 592and routing the structural tubes 506 through the stringers 92, theactuation pedal assembly 516 and the lineal linkage assembly 514 areelevated relative to operate within the height dimension of theframework 32 and provides added clearance for the high capacitycargo/container dolly 30 to pass over objects, ramp transitions, andother terrain irregularities. If the framework 32 clears a givenobstacle, so do the lineal linkage assemblies 514. Therefore, if theframework 32 clears an obstacle, operating personnel need not concernthemselves with whether the lineal linkage assemblies 514 will clear.The welding of the reinforcement housings 594 and the structural tubes506 to the side beam assemblies 42 and the stringers 92, respectively,maintains the strength of the side beam assemblies 42 and the stringers92 so that the notches 592 and 596 do not significantly diminish thestructural load capacity of the high capacity cargo/container dolly 30.

Referring to FIG. 33 and again to FIG. 29 , the auxiliary retractionmechanism 504 is described in greater detail according to an embodimentof the disclosure. In some embodiments, the auxiliary retractionmechanism 504 includes a rotatable linkage 602 that extends axially(i.e., parallel to the centerline 90 of the high capacitycargo/container dolly 30) and having a proximal end 604 and a distal end606 and supported by pillow blocks 608. An actuation handle 612 iscoupled to the proximal end 604, accessible from the forward beamassembly 36. Alternatively, the actuation handle 612 may be accessiblefrom the rearward beam assembly 38 (not depicted). In some embodiments,two actuation handles 612 may be utilized—one accessible from theforward beam assembly 36 and a second accessible from the rearward beamassembly 38 (not depicted). An actuation plate 614 is coupled to therotatable linkage 602, for example at or near the distal end 606(depicted), extending in close proximity to the lineal linkageassemblies 514 of the foot actuated retraction mechanisms 502. In thedepicted embodiment, the actuation plate 614 includes recesses 616through which the rods 562 of the lineal linkage assemblies 514 pass.Each rod 562 may be fitted with a contact structure 618 (e.g., clampblocks 622 a, 622 b depicted) adjacent the actuation plate 614. In someembodiments, a limit structure 624 extends from the actuation plate 614.The limit structure 624 may include stops 626 configured to engage thestructural tubes 506.

In operation, the auxiliary retraction mechanism 504 offers analternative to selectively retract the retractable side stop(s) 68 on agiven side beam assembly 42 a or 42 b, for example when the desired footactuated retraction mechanisms 502 is inaccessible. In some embodiments,an operator actuates the auxiliary retraction mechanism 504 by rotatingthe actuation handle 612 in one of a first rotational direction 642 or asecond rotational direction 644. Rotation of the handle 612 causesrotation of the rotatable linkage 602 and actuation plate 614, whichcauses the actuation plate 614 to engage and push against one of theclamp blocks 622 a, 622 b. The pushing of the clamp blocks 622 a or 622b causes translation of one of the lineal linkage assemblies 614 foractuation of the associated foot actuated retraction mechanism 502. Inthe depicted embodiment, rotation of the actuation handle 612 in thefirst rotational direction 642 causes the actuation plate 614 to engagethe clamp blocks 622 a and actuate the foot actuated retractionmechanism 502 a for retraction of the retractable side stop(s) 68 on theside beam assembly 42 a; rotation of the actuation handle 612 in thesecond rotational direction 644 causes the actuation plate 614 to engagethe clamp blocks 622 b and actuate the foot actuated retractionmechanism 502 b for retraction of the retractable side stop(s) 68 on theside beam assembly 42 b. The actuation handle 612 may be actuated bygrasping and turning the handle 612, or by actuating the handle 612 witha foot.

Referring to FIG. 34 , the self-locking roller assembly 66 is depictedaccording to an embodiment of the disclosure. The self-locking rollerassembly 66 and alternative embodiments thereof are presented in greaterdetail at U.S. patent application Ser. No. 16/061,976, filed Jun. 13,2018, owned by the owner of the present application, the contents ofwhich are hereby incorporated by reference herein in their entiretyexcept for patent claims contained therein.

Referring to FIGS. 34 through 37 , the self-locking roller assembly 66for a roller conveyor is depicted according to an embodiment of thedisclosure. The self-locking roller assembly 66 includes a roller 662, alocking mechanism 664, and an actuation mechanism 665 for unlocking theself-locking roller assembly 66. The locking mechanism 664 includes alock shaft 739, a lock clutch 740 that can be translated over the lockshaft 739, and at least one locking protrusion 737 that extends radiallyoutward from the lock shaft 739. The lock clutch 740 is affixed to theroller 662. In some embodiments, the locking mechanism 664 includes abiasing element 742. For the self-locking roller assembly 66, theactuation mechanism 665 is a lateral actuator assembly, configured tolaterally translate the roller 662 and affixed lock clutch 740 over thelock shaft 739.

The self-locking roller assembly 66 may be supported by a roller mount750 including a first support 752 and a second support 754. The lockshaft 739 of the locking mechanism 664 is suspended at opposing ends bythe first support 752 and the second support 754. The roller 662 isselectively rotatable about a rotation axis 756. The lock shaft 739 ofthe locking mechanism 664 defines a shaft axis 772 that extends parallelto the rotation axis 756, the lock shaft 739 including a first endportion 774 that is mounted to the first support 752 and a second endportion 775 mounted to the second support 754. In the depictedembodiment, the lock shaft axis 772 and the rotation axis 756 arecoaxial. Also in the depicted embodiment, the lock shaft 739 andprotrusion(s) 737 are in a static relationship relative to the first andsecond supports 752 and 754. That is, the lock shaft 739 neither rotatesnor laterally translates relative to the supports 752 and 754. Instead,the roller 662 and the lock clutch 740 are translatable relative to thelock shaft 739 along the lock shaft axis 772. By this translation, theroller 662 is can be configured in one of a lock position 782 (depictedin FIGS. 34 through 37 ) and an unlock position 784 (depicted in FIGS.12 through 14A). In the depicted embodiment, the actuator assembly 665is configured to laterally translate the roller 662.

The lock clutch 740 is coupled to and in fixed rotational relationshipwith the roller 662, with the lock clutch 740 being selectivelyengageable with the protrusion(s) 737. In some embodiments, the lockclutch 740 includes a plurality of fingers 722 that define a pluralityof notches 724 therebetween (FIG. 35 ). The locking mechanism 664 mayinclude at least one protrusion 737 that extends within the plurality ofnotches 724 to engage the plurality of fingers 722 when the lockingmechanism 664 is in the lock position 782, thereby preventing the roller662 from rotating about the rotation axis 756. The roller 662 and lockclutch 740 translate parallel to the lock shaft axis 772 to pass overthe protrusion(s) 737, thereby disengaging the protrusion(s) 737 fromthe plurality of notches 724 and the plurality of fingers 722 of thelock clutch 740 when the locking mechanism 664 is in the unlock position784, thereby enabling the roller 662 to rotate about the rotation axis756. In the depicted embodiment, protrusion(s) 737 extends radiallyoutward relative to the lock shaft axis 772 for selective engagementwith the plurality of fingers 722. In some embodiments, and theplurality of fingers 722 extend radially inward from a continuous outerring portion 728 of the lock clutch 740.

In the depicted embodiment, the biasing element 742 is coupled to thelock shaft 739 to bias the locking mechanism 664 and actuator assembly665 into the lock position 782. In some embodiments, the biasing element742 may be one of a spring 732 (depicted) or a repelling magneticarrangement. By way of non-limiting example, the spring 732 may be oneof a coil spring (depicted), a bow spring, and an elastic plug orsleeve. In the depicted embodiment, the spring 732 acts against theprotrusion(s) 737 for the biasing. In some embodiments, theprotrusion(s) 737 is defined by a pin 734 that extends radially outwardrelative to the lock shaft axis 772, the pin 734 and spring 732 beingconfigured to so that the spring 732 acts against the pin 734 to biasthe locking mechanism 664.

Referring to FIGS. 38 through 40, 44, and 45 , the actuator assembly 665is depicted in more detail according to an embodiment of the disclosure.The actuator assembly 665 includes a lever 738, at least one cam 792, ayoke 794, a stop 796, and a pivot pin 798. The lever 738 is fixedlycoupled to the cam(s) 792, for example by welding or other conventionalcoupling arrangements available to the artisan. In the depictedembodiment, the lever 738 is formed of a round rod 786 having a circularcross-section 787 (FIG. 43A) that defines an arcuate portion 788. Thecam(s) 792 includes an arcuate surface 702 and a stop engagement surface704. In the depicted embodiment, the yoke 794 and stop 796 arediametrically opposed about the lock shaft 739 of the locking mechanism664, and attached to the lock shaft 739 with fasteners 706 that passthrough the yoke 794, lock shaft 739, and stop 796. The cam(s) 792 arepivotally mounted to the yoke 794 with the pivot pin 798, the pivot pin798 defining a pivot axis 708, the pivot axis 708 extending in adirection that is orthogonal to the lock shaft axis 772. The lever 738is offset from the pivot axis 708 by a distance X (FIG. 37 ).

Referring to FIGS. 41 through 45 , the self-locking roller assembly 66is depicted in the unlock position 784 according to an embodiment of thedisclosure. The lever 738 and cam(s) 792 are rotatable about the pivotaxis 708 for actuation of the locking mechanism 664. In the unlockposition 784, the arcuate surface 702 is extended laterally against theend of the roller 662 to laterally translate the roller 662. When in thelock position 782, the lever 738 extends through a plane 776 inclusiveof an upper-most tangent line 778 (FIGS. 36, 42, 43, and 43A) of theroller 662 and extending parallel to the pivot axis 708, the plane 776extending above the first and second supports 752 and 754. In the unlockposition, the lever 738 is rotated laterally outward and away from theroller 662 so that an upper extremity of the lever 738 approaches plane776.

In operation, when the actuator assembly 665 is in the lock position782, the lock shaft 739 and the lock clutch 740 of the locking mechanism664 are coupled, thereby preventing the roller 662 from rotating aboutthe rotation axis 756 (FIGS. 35 through 37 ). When an object 760 (FIGS.41, 43, and 43A) passes over the self-locking roller assembly 66, theobject slides up onto the arcuate portion 788 of the lever 738, therebygenerating a downward force FD on the lever 738 due to gravity. Thedownward force FD causes a moment M about the pivot axis 708 because ofthe offset distance X between the lever 738 and the pivot axis 708. Inthis way, the actuator assembly 665 is pivoted about the pivot axis 708into the unlock position 784, causing the cam(s) 792 to rotate towardand exert a lateral force FL on roller 662. The arcuate portion 788 ofthe lever rotates laterally away from the roller 662, which may causethe arcuate portion 788 to slide against a contacting surface 762 of theobject 760 as it pivots downward toward the plane 776 (FIG. 43A). Thecircular cross-section 787 of the round rod 786 facilitates the slidingaction against the contacting surface of the object.

Actuation of the actuation mechanism 665 causes the arcuate surface 702of the cam(s) 792 to slidingly engage with the end of the roller 662 toexert the lateral force FL and laterally translate the roller 662relative to the locking mechanism 664 along the lock shaft axis 772. Thelateral translation is depicted by arrow 764. Accordingly, theupper-most tangent line 778 of the roller 662 may also slide laterallyagainst the contacting surface 762 of the object, as depicted in FIG.43A. The lateral translation of the roller 662 causes the lock clutch740 to pass over the protrusion(s) 737 of the locking mechanism 664(FIGS. 41-43 ), thereby disengaging the lock clutch 740 from theprotrusion(s) 737 and enabling the roller 662 to rotate about therotation axis 756. The spring 732 biases the roller 662 laterally towardthe actuator assembly 665, so that in the lock position 782, the stopengagement surface 704 of the cam(s) 792 is engaged against the stop796.

Referring to FIGS. 46 through 49 , the deck modules 76 of the highcapacity cargo/container dolly 30 are depicted in greater detailaccording to embodiments of the disclosure. The outer frame 34 andstringers 92 of the framework 32 define an upper registration surface802 of the high capacity cargo/container dolly 30. In some embodiments,the tineways 74 are attached to the upper registration surface 802. Theupper registration surface 802 may be planar. The tineways 74 andframework 32 define a plurality of openings 804 at the upperregistration surface 802, the outlines of which are identified in FIG.46 with cross-hatched lines.

The deck modules 76 of the roller deck 75 are configured to mount to theupper registration surface 802 of the framework 32, for example withfasteners 806 that pass through mounting holes 808 to fasten the deckmodules 76 to the framework 32. Each of the deck modules 76 include alower base plate 812, an upper tread plate 814 that extends over and isaffixed (e.g., welded) to the lower base plate 812. The deck modules 76may include stiffener structures 818, such as channels 817 and gussetplates 819 affixed (e.g., welded) to the lower base plate 812.

The deck modules 76 further include a plurality of components 820 forsecuring cargo to the roller deck 75. Such fixtures include theself-locking roller assemblies 66 and the swivel casters 472, as well aspallet stop brackets 822, and lift and lay pallet stops 824. The swivelcasters may be toe guard casters 826. Some of the lift and lay palletstops 824 may include added spacer blocks 832 (to reduce containerplay), rigid vertical restraints 834, spring-loaded vertical restraints836, or fall away lift and lay pallet stops 838. The components 820 aremounted to the lower base plate 812, for example with fasteners 842 orby welding, and extend or can be configured to extend through apertures844 or edge cutouts 846 defined on the upper tread plate 814. The uppertread plate 814 may also include access cutouts 848 for accessing themounting holes 808.

Each deck module 76 may be configured to cover one or more of theopenings 804. In some embodiments, there are four different deck moduleconfigurations: a first corner module 76 a, a center module 76 b, asecond corner module 76 c, and a middle module 76 d. The roller deck 75includes one middle module 76 d and two each of the first corner module76 a, center module 76 b, and second corner module 76 c, for a total ofseven deck modules 76. The first corner module 76 a may be used at botha forward-right corner position 852 and a rearward left corner position854 of the framework 32. The second corner module 76 c may be used atboth a forward-left corner position 856 and a rearward-right cornerposition 858 of the framework 32. The center module 76 b may be used atboth a forward-center position 862 and a rearward-center position 864.The middle module 76 d may be configured for positioning betweentineways 74.

The deck modules 76 are also configured so that the lower base plates812 effectively cover the openings 804. That is, some edge portions 872of the lower base plates 812 extend horizontally (i.e., parallel to theplane defined by the x- and y-axes of the Cartesian coordinate 80 ofFIG. 1 ) and overlap onto the stringers 92 and outer frame 34, to whichthe deck modules 76 are fastened. Other edge portions 874 of the lowerbase plates 812 extend vertically and are closely adjacent to thetineways 74. Where necessary, the lower base plates 812 define edgecutouts 876 that trace around components that need to extend through thebase plates 812 (e.g., to trace around the retractable side stops 68).

Functionally, the use of deck modules 76 enable selected sections to beremoved, repaired, or replaced without need of removing or replacing theentire roller deck 75. Also, the use of the first corner module 76 a,center module 76 b, and second corner module 76 c in one of twopositions of the roller deck 75 makes these components interchangeable.Accordingly, fewer types of deck modules 76 need to be tooled,fabricated, and inventoried than if the deck modules 76 were notinterchangeable. By effectively covering the openings 804, the lowerbase plates 812 protect the components 820 from debris that impinges theunderside of the roller deck 75 (e.g., from road spray).

Each of the additional figures and methods disclosed herein can be usedseparately, or in conjunction with other features and methods, toprovide improved devices and methods for making and using the same.Therefore, combinations of features and methods disclosed herein may notbe necessary to practice the disclosure in its broadest sense and areinstead disclosed merely to particularly describe representative andpreferred embodiments.

Various modifications to the embodiments may be apparent to one of skillin the art upon reading this disclosure. For example, persons ofordinary skill in the relevant arts will recognize that the variousfeatures described for the different embodiments can be suitablycombined, un-combined, and re-combined with other features, alone, or indifferent combinations. Likewise, the various features described aboveshould all be regarded as example embodiments, rather than limitationsto the scope or spirit of the disclosure.

Persons of ordinary skill in the relevant arts will recognize thatvarious embodiments can comprise fewer features than illustrated in anyindividual embodiment described above. The embodiments described hereinare not meant to be an exhaustive presentation of the ways in which thevarious features may be combined. Accordingly, the embodiments are notmutually exclusive combinations of features; rather, the claims cancomprise a combination of different individual features selected fromdifferent individual embodiments, as understood by persons of ordinaryskill in the art.

Any incorporation by reference of documents above is limited such thatno subject matter is incorporated that is contrary to the explicitdisclosure herein. Any incorporation by reference of documents above isfurther limited such that no claims included in the documents areincorporated by reference herein. Any incorporation by reference ofdocuments above is yet further limited such that any definitionsprovided in the documents are not incorporated by reference hereinunless expressly included herein.

Unless indicated otherwise, references to “embodiment(s)”, “disclosure”,“present disclosure”, “embodiment(s) of the disclosure”, “disclosedembodiment(s)”, and the like contained herein refer to the specification(text, including the claims, and figures) of this patent applicationthat are not admitted prior art.

For purposes of interpreting the claims, it is expressly intended thatthe provisions of 35 U.S.C. 112(f) are not to be invoked unless thespecific terms “means for” or “step for” are recited in the respectiveclaim.

What is claimed is:
 1. A high capacity cargo/container dolly,comprising: a framework defining a centerline and including an outerframe having opposed side beam assemblies that extend parallel to saidcenterline; a retractable side stop disposed proximate one of saidopposed side beam assemblies, said retractable side stop including ahousing and a plunger assembly translatable in a vertical directionwithin said housing; and an actuation linkage defining a rocker axis andhaving pivotal coupling to the high capacity cargo/container dolly aboutsaid rocker axis, said actuation linkage including: a first arm thatextends in a first lateral direction from said rocker axis, said firstarm being coupled to said plunger assembly of said retractable sidestop; a second arm that extends in a second lateral direction from saidrocker axis to a free end, said second lateral direction being generallyopposite said first lateral direction; and a counterweight affixed tosaid second arm at said free end for generation of inertial momentsabout said rocker axis during dynamic loads that counters systeminertial moments about said rocker axis caused by said dynamic loads. 2.The high capacity cargo/container dolly of claim 1, wherein saidcounterweight and said second arm are unitary.
 3. The high capacitycargo/container dolly of claim 1, comprising a foot actuated retractionmechanism operatively coupled to said retractable side stop forreconfiguration of said retractable side stop from a deployedconfiguration to a retracted configuration, said foot actuatedretraction mechanism including a rotatable shaft that is rotatable abouta rotation axis, wherein said actuation linkage is pivotally mounted tosaid rotatable shaft for said pivotal coupling to the high capacitycargo/container dolly, said rocker axis of said actuation linkage beingconcentric with said rotation axis of said rotatable shaft.
 4. The highcapacity cargo/container dolly of claim 3, wherein said foot actuatedretraction mechanism includes a cam arm mounted to and in fixedrotational relation with said rotatable shaft, said cam arm configuredto exert a force on said actuation linkage when said foot actuatedretraction mechanism is actuated.
 5. The high capacity cargo/containerdolly of claim 3, wherein said foot actuated retraction mechanismincludes: a lineal linkage assembly coupled to and configured to rotatea rotation linkage assembly, said lineal linkage assembly extendinglaterally through said framework; and an actuation pedal assemblycoupled to said lineal linkage assembly for translating said lineallinkage assembly to rotate said rotation linkage assembly and actuatesaid retractable side stop.
 6. The high capacity cargo/container dollyof claim 1, wherein said retractable side stop includes: a stop bracketmounted to said housing that defines an uppermost position of saidplunger assembly; a stop finger coupled to said plunger assembly anddefining a vertical stop plane; and a catch assembly including a hookthat extends upward from a lever, said lever being mounted to a pivotthat is coupled to said plunger assembly, said lever including alaterally inward portion that defines a length having a lateraldimension that extends from said pivot toward said centerline of saidframework, said laterally inward portion of said lever extendingunderneath said stop bracket.
 7. The high capacity cargo/container dollyof claim 1, wherein said retractable side stop includes: a rollerlinkage assembly pivotally coupled to said housing about a pivot axis,said roller linkage assembly including: a pivot arm pivotal about saidpivot axis and having a first end and a second end, a first rollerdisposed at said first end of said pivot arm that contacts said plungerassembly, and a second roller disposed at a second end of said pivot armthat extends above said registration plane; and an actuation memberoperatively coupled to said plunger assembly and configured to contactsaid roller linkage assembly when said plunger assembly is translateddownward into said housing and if said pivot arm does not rotate aboutsaid pivot axis due to gravity.
 8. The high capacity cargo/containerdolly of claim 7, wherein said retractable side stop includes: a stopbracket mounted to said housing that defines an uppermost position ofsaid plunger assembly; a stop finger coupled to said plunger assemblyand defining a vertical stop plane; and a catch assembly including ahook that extends upward from a lever, said lever being mounted to apivot that is coupled to said plunger assembly, said lever including alaterally inward portion that defines a length having a lateraldimension that extends from said pivot toward said centerline of saidframework, said laterally inward portion of said lever extendingunderneath said stop bracket, wherein: in a capture configuration, saidlaterally inward portion of said lever of said catch assembly is engagedand in contact with said stop bracket, said hook of said catch assemblyextending above said registration plane and a bend portion of said hookextends laterally inward relative to said vertical stop plane; in arelease configuration, said bend portion of said hook is positionedentirely laterally outward relative to said vertical stop plane, saidlaterally inward portion of said lever being configured to disengagefrom contact with said stop bracket to attain said release configurationwhen said plunger assembly is translated axially downward relative tosaid uppermost position; and said laterally inward portion of said leveris configured to disengage from contact with said stop bracket when saidplunger assembly is translated a minimum downward vertical displacementfrom said uppermost position.
 9. The high capacity cargo/container dollyof claim 8, wherein said minimum downward vertical displacement is in arange of ¾ inch to 1 inch inclusive.
 10. A high capacity cargo/containerdolly, comprising: a framework defining a centerline and including anouter frame having opposed side beam assemblies that extend parallel tosaid centerline; a retractable side stop disposed proximate a first ofsaid opposed side beam assemblies, said retractable side stop includinga housing and a plunger assembly translatable in a vertical directionwithin said housing; a foot actuated retraction mechanism operativelycoupled to said retractable side stop for reconfiguring said retractableside stop from a deployed configuration to a retracted configuration,said foot actuated retraction mechanism including a rotatable shaft thatis rotatable about a rotation axis, and an actuation linkage pivotallymounted to said rotatable shaft, said rocker axis of said actuationlinkage being concentric with said rotation axis of said rotatableshaft, said foot actuated retraction mechanism including a cam armmounted to and in fixed rotational relation with said rotatable shaft,said cam arm configured to exert a force on said actuation linkage whensaid foot actuated retraction mechanism is actuated.
 11. The highcapacity cargo/container dolly of claim 10, comprising a torque returnspring attached to said rotatable shaft of said foot actuated retractionmechanism, said torque return spring being arranged to resist dynamicloads on said foot actuated retraction mechanism.
 12. The high capacitycargo/container dolly of claim 11, comprising: a lineal linkage assemblycoupled to and configured to rotate said rotatable shaft, said lineallinkage assembly extending laterally through said framework; and anactuation pedal assembly coupled to said lineal linkage assembly fortranslating said lineal linkage assembly to rotate said actuationlinkage for actuation of said retractable side stop.
 13. The highcapacity cargo/container dolly of claim 10, comprising: a roller deckcoupled to said framework including a plurality of swivel casters havingupper extremities that define and are coplanar with a registrationplane, said registration plane being generally horizontal; a stop fingercoupled to said plunger assembly and defining a vertical stop plane; anda roller linkage assembly pivotally coupled to said housing about apivot axis, wherein: said vertical stop plane intersects saidregistration plane at an intersection line, said intersection line beingsubstantially parallel to said centerline; said retractable side stop isconfigurable in a deployed configuration and a retracted configuration;in said deployed configuration, said roller linkage assembly extendsthrough said registration plane and is disposed laterally outwardrelative to said centerline from said intersection line; and in saidretracted configuration, said roller linkage assembly is locatedcompletely below said registration plane.
 14. The high capacitycargo/container dolly of claim 13, wherein, in transitioning saidretractable side stop from said deployed configuration to said retractedconfiguration, said roller linkage assembly is rotated completely belowsaid registration plane without crossing said intersection line.